Rotary vane device for compressor, motor or engine

ABSTRACT

An integral vane compressor and vane motor. At least three vanes are pinned to a central hub and extend through respective slots in a generally cylindrical drum with its axis parallel to and displaced radially from that of said hub, the slots guiding the radial position of the vanes. Synchronizing means, such as a gear train, cause the hub and drum to rotate in the same direction and at the same speed, with the vanes reciprocating and oscillating in the guide slots. A housing encloses the vanes and cooperates with them and the drum to provide a series of working spaces, one for each vane to compress or expand a fluid. Intake and exhaust ports lead fluid into and from the working spaces.

United StatessPatent 1 1 n] 3,813,191 Foster i 1 May 28,1974

1 1 ROTARY VANE DEVICE FOR COMPRESSOR, MOTOR OR ENGINE Berry W. Foster,2415 Thomas Ave., Redondo Beach, Calif. 90278 Filed: Apr. 12, 1973Appl.- No.: 350,632

Related US. Application Data Continuation-impart of Ser. No. 268,866,May 1, 1972, Pat. No. 3,747,573, which is a continuation of Ser. No.41.008, May 22, 1970.

Inventor:

References Cited UNlTED STATES PATENTS 9/1912 Carroll 417/348 3/1919417/348 8/1972 417/406 7/1973 Foster 418/137 COMPRESSOR DISCHARGE FORHIGH PRESSURE COMPRESSOR lNTAKE FOR, LOW -PRESSURE GASES PrimaryExaminer-C. .1. Husar Attorney, Agent, or Firm-Owen, Wickersham &

Erickson [57] ABSTRACT An integral vane compressor and vane motor. Atleast three vanes are pinned to a central hub and extend throughrespective slots in a generally cylindrical drum with its axis parallelto and displaced radially from that of said hub, the slots guiding theradial position of the vanes. Synchronizing means, such as a gear train,cause the hub and drum to rotate in the same direction and at the samespeed, with the vanes reciprocating and oscillating in the guide slots.A housing encloses the vanes and cooperates with them and the drum toprovide a series of working spaces, one for each vane to compress orexpand a fluid. lntakeand exhaust ports lead fluid into and from theworking spaces.

2 Claims, 9 Drawing Figures Moron INTAKE FOR HOT HIGH PRESSURE GASES\MOTOR EXHAUST FOR GASES PATENTEUMY 2 w 3.8 13191 sum 1 (IF. 7

PATENTEDmzs 1911 3.813.191 SHEET '4 0f 7 FIG. 5

PMENTEMHB I914 38131191 SHEEI 7 0F 7 COMPRESSOR DISCHARGE MOTOR INTAKEFOR FOR HIGH -PRESSURE HOT HIGH PRESSURE OASES\ GASES l 4313 COMPRESSORINTAKE \MOTOR EXHAUST EOR EOR LOW-PRESSURE I OASES OASES ROTARY VANEDEVICE FOR COMPRESSOR, MOTOR ENGINE No. 3,747,573 which was acontinuation of application Ser. No. 41,008 filed May 22, I970.

BACKGROUND AND SUMMARY OF THE INVENTION This invention relates to anintegral vane compressor and vane motor.

A feature of the rotary vane device of this invention is that the vanesare pinned to a central hub-shaft, and it has a separate circular drumto help transmit torque through the vanes and to guide the radialdirection of the vanes. The'vanes are pinned at their centers of gravityto the central hub-shaft, so that they can oscillate back and forth asthe central hub-shaft rotates; as a result, the mechanism is kept indynamicbalance. The central hub shaftsupports the full centrifugal pullof the vanes; consequently, they have no friction drag at their tipswhere they nearly. (but not quite) touch the housing. y

The central hub-shaft and the'circular drum both rotate at the samespeedand in the same direction, but the center of rotation of the circulardrum is offset from the center of rotation of the central hub-shaft.-Theradius of the circular drum is smaller than the radial distance from thehub center to the tips of the extended vanes in every position of theirrotation. The circular drum preferably has equally spaced axial slots atits outer periphery, one for each vane; these axial slots are preferablyjust big enough so that the vanes are forced to oscillate andreciprocatein themas the drum and shaft rotate. As the shaft and drum rotate andthe vanes are forced to rotate and oscillate, their tipsform acircumscribed surface.

The housing of my new rotaryvanedevice is slightly larger than thecircumscribed surface of the vanes; thus there is no friction betweenthevanes and the housing. The housing may be provided with an intake portand an exhaust port. The space bounded between two adjacent vanes, thecylindrical surface of the drum between these vanes, and the cylindricaland disc surfaces of the housing constitutes the working space. Theremay be three or more working spaces in each device, and the volume ofeach working space varies as the drum and the hub-shaft rotate in thestationary housing. For example, the maximum volume of this workingspace is l80 out of phase with its minimum volume. I

In the compressor portion, the intake port is closed by a rotary vanejust after the working space is largest; as the vanes and drum rotate,decreasing the volume of the working space, they give an isentropiccompression of the trapped gases. The compressed gases are then forcedout of the workingspace through a discharge port located where theworking space is smallest.

In the motor portion, used to expand compressed pressed gas and expandit until the working space is at its largest volume;then the exhaustport opens to exhaust low pressure gases asthe working space becomessmaller.

The integral vane compressor and vane motor have a compressor intakeport for low pressure gases, a compressor discharge port forhigh-pressure gases. :1 motor intake port for hot high-pressure gasesand a motor exhaust port for exhaust gases. The compressor intake portand the motor exhaust port may connect to the same working space. Ablower may be used to force a fresh charge into the intake port. A jetpump action of the exhaust gases flowing out and the fresh chargeflowing in may exhaust, charge, and scavenge the common working spacefor the intake and exhaust ports. This integral vane compressor and vanemotor may be used similar to a turbocharger. Also, it may be usedsimilar to a gas turbine, wherein the compressor and motor use the samewheel; The working spaces for the vane motor may expand to a largervolume than the intake volume for they vane compressor; thus the devicewill generate shaft power similar to a gas turbine. As an alternatedesign the working spaces for the vane motor may expand to a volumeequal to or only slightly larger than the intake volume for thecompressor; in this case the vane device acts like a turbo-charger oragas turbine gas generator which may supply gases to a free-running gasturbine.

' BRIEF DESCRIPTION OF THE DRAWINGS FIG. 3 is a view in section takenalong the line 3-3 in FIG. 2, showing the end view of the gears.

FIG. 4 is a fragmentary view in section of a modified form of the devicethat may be used as a compressor or a motor,.depending on whether thehub-shaft and the drum rotate clockwise, when it acts as a compressor,or counterclockwise, when it acts as a motor or steam engme..

FIG. 5 is an end view in section of the engine of FIG. 4 showing theadjustable sliding circular valve for regulating the cutoff point forsteam or compressed gas expan'sion in the vane motor.

FIG. 6 is a fragmentary detail view of a portion of the motor, showing aspring seal ring to contain the lubrieating oil inside the'drum.

FIG. 7 is a fragmentary enlarged view, partly diagrammatic, of the gearbox with part of the hub shaft broken away to show parts otherwiseobscured.

FIG. 8 is a diagram relative to the geometry of the vanes, hub, and drumas they rotate.

FIG. 9 is a block flow diagram showing how the rotary vane device maybeused as an integral vane compressor and vane motor.

DESCRIPTION OF THE PARTS AND THEIR OPERATION I The vane engine 10 ofFIGS. I to 3 comprises a gen- 3 erally cylindrical housing 11. Ahub-shaft 12 rotates about a center line 13, having its bearings on orsupported by the housing 11 (FIG. 2). In the design shown, the hub-shaft12 has eight equally spaced piano hinges 21, 22, 23, 24, 25, 26, 27, 28,(which may be pinned at the ends only or as shown) and eight vanes 31,32, 33, 34, 35, 36, 37, and 38 are pinned at their center of gravity torespective piano hinge points 21, 22, 23, 24, 25, 26, 27, and 28 bymeans of shafts 41, 42, 43, 44, 45, 46, 47, and 48. Each of the vanes31, 32, 33, 34, 35, 36, 37, 38 may have a counter mass 51, 52, 53, 54,55, 56, 57, 58, so that as the vanes oscillate about their respectiveshafts 41, 42, 43, 44, 45, 46, 47, 48, the hubshaft 12 remains indynamic balance as it rotates. Although eight vanes are shown in FIG. 1,any number of equally spaced vanes greater than three may be used.

A drum 14 rotates about a center line 15 which is displaced from the hubcenter line 13 by the distance y. The drum 14 has its bearing on thehousing 11. The drum 14 and the hub-shaft 12 are synchronized to rotatein the same direction and at the same rotating speed. The drum 14 hasslots 61, 62, 63, 64, 65, 66, 67, 68 at its outer diameter, and theseslots are just large enough for the corresponding vanes 31, 32, 33, 34,35, 36, 37, 38 to slide and oscillate in as the hub-shaft 12 and thedrum 14 rotate. Between adjacent axial slots 61, 62, 63, 64, 65, 66, 67,68 there may be gusseted arch or beam sections 71, 72, 73, 74, 75, 76,77, 78 with cooling ports or tubes 79. The drum 14 may have discs 16 and17 (FIG. 2) at its ends for supporting the gusseted arc sections 71, 72,73, 74, 75, 76, 77, 78. The discs 16 and 17 also support the bearings 18and 19 for the drum 14 on the housing 11. The disc 16 may also beprovided with an internal gear 80 (FIG. 3).

The mechanism for synchronizing the hub-shaft 12 and the drum 14 maycomprise the internal gear 80 and a meshing spur gear 81, which is keyedto a shaft 82 that has its bearings on the housing 11. Also keyed toshaft 82 is a second spur gear 83. The spur gear 83 may be meshed with apinion gear 84, which is also meshed to a third spur gear 85, or, asshown in FIG. 7, the gear 84 is keyed to a shaft 84a that also carries agear 84b meshed to the gear 85. The spur gear 85 is keyed to thehub-shaft 12. The pinion gear 84 has its shaft bearings on the housing11. The pitch diameter and teeth of the gears 80, 81, 83, 84, and 85 areprescribed so that the hub-shaft 12 and the drum 14 are synchronized torotate in the same direction and at the same rotating speed.

As shown in FIG. 7, the gears have the following pitch diameters:

diameter and the pitch diameters are related so that 01/02 X 03/04 X D.'Dfi Power may be transmitted through the shaft 12 or the shaft 82 orboth of them. The housing 11 may be provided with cooling fins 86.

For the engine device of FIG. 1, the housing 11 may be provided with anintake scavenging and exhaust port 87. A fan 88, which is keyed to thehub-shaft 12, may be used to blow a fresh charge of air through the openport 87 to help scavenge the expanded gases out of the exhaust, to coolthe vanes 31, 32, 33, 34, 35, 36, 37, and 38 and to cool the outersurface of each drum beam section 71, 72, 73, 74, 75, 76, 77, 78 when itis at the port 87. Also. the fan air flows past the cooling fins 86 tocool the engine housing 11 and blows air through the cooling passages 79between the gussets and the arcuate segments in the beam elements 71,72, 73, 74, 75, 76, 77, and 78.

The hub-shaft 12 rotates clockwise, and when, for example, the vane 36moves past the position 89 of the housing 11, a fresh charge is trappedin a working space 96 bounded by the adjacent vanes 36 and 37, the outersurface of the beam element 76, and the inner surface of the housing 11between the tips of the vanes 36, 37 and side disc section of thehousing 2. Each of the adjacent vanes 31, 32, 33, 34, 35, 36, 37, 38 hasa working space 91, 92, 93, 94, 95, 96, 97, 98. (For a three vane enginethere would be three working spaces; for every vane, no matter how many,there is a corresponding working space.) A fuel injector 99 may injectfuel into each working space 91, 92, 93, 94, 95, 96, 97, 98, in turn asit moves past it.

As the hub-shaft 12 and the drum 14 move clockwise, they force the vanes31, 32, 33, 34, 35, 36, 37, 38 to follow a prescribed movement and theworking space 91, 92, 93, 94, 95, 96, 97, 98 becomes smaller, thuscompressing the gases trapped in it in a manner approaching isentropiccompression. When each space is in the top position (where the space 91is in FIG. 1), it has been reduced to its smallest volume, and a sparkignition system 100 is timed to explode the fuel in the space 91 andheat it substantially by a constant volume process to increase itspressure and force the vanes to turn the hub-shaft 12 clockwise, so thehot gases will expand and do work on the engine shaft. When the vanes31, etc., reach the position 101 of the housing 11, the hot expandedgases in the space 91, etc., are exhausted centrifugally by thecentrifugal action of rotation. Also, the fan 88 forces exhaust gases toflow axially out of the port 87.

ln FIGS. 4 and 5 the rotary vane compressor or motor has most of thesame parts as the engine 10 and are given the same reference numerals.The basic differences are that the fuel injector 99 and the sparkignition system 100 are eliminated, and in place of the common exhaust,scavenging, and intake port 87 shown for the engine 10, the housing 111of the compressor or motor 110 has an intake port 112 separate from thedischarge port 113, and these ports 112 and 113 are locateddiametrically opposite each other. Also, the vanes 31, 32, 33, 34, 35,36, and 37 are practically inside the drum 114, when its respectiveworking space 191, 192, 193, 194, 195, 196, 197, 198 is at its minimumvolume, which is equal to the working tolerances between the housing 111and the drum 114 multiplied by the vane width.

When operating as a vane compressor 110, the intake port 112 is closedas the vane 31, 32, etc., is forced past the edge 115 of the port 112 bymeans of clockwise rotation of hub-shaft 12 and the drum 114. Theworking space 191,192, etc., may be close to its largest volume justafter the vane 31, 32, etc., closes the intake port 1 5 112 at thestation 115. As the compressor rotates clockwise, the working space 191,192, etc., is reduced, and the trapped gases are compressedapproximately adiabatically until the vanes 31, 32, etc., move past thestation 116 in the housing 111 to open the space 191, 192, etc., to thedischarge port 113. The compressed gases are preferably forced out ofthe space 191, 192, etc., through the discharge port 113 into acompressed gas accumulator (not shown). When the vanes 31, 32, etc.,rotate past a station 117, a small volume of compressed gas is trappedin the space 191, 192, etc., this trapped compressed gas expandsapproximately isentropically and does work on the vanes 31, 32, etc., asthe space 191, 192, etc., increases. When the vanes 31, 32, etc., pass astation 118, the compressed gas in the space 191, 192, etc., issubstantially equal to the pressure of the gas in the intake port 112.In order to increase the volumetric efficiency of the compressor, thevolume of space 191, 192, etc., as the vane 31, 32, etc., moves past thestation 117 should be kept to a minimum.

When the device 110 is operation as a vane motor or steam engine, themotor turns in a counterclockwise direction. Compressed gas or steam,etc., flows from the accumulator, not shown, through the port 113, whichis now the intake port, into the working space 191, 192, etc. After thevanes 31, 32, etc., move past the station 116, the compressed gases aretrapped in the working space 191, 192, etc. As the motor rotatescounterclockwise, the working space 191, 192, etc., increases in volumeand the compressed gases expand approximately isentropically'to do workon the vanes 31, 32, etc., until they move past the station 115 to openport 112, which is now the exhaust port. When the exhaust port 112 isopen, the pressure in theworking spaces 191, 192, etc., is substantiallythe same as the gases in the exhaust port 112, except when the cutoffpoint is increased. After the vane 31, 32, etc., moves past the station118, gases are trapped in the space 191, 192, etc.; this trapped gas isapproximately isentropically compressed back to the pressure in theaccumulator as the working space 191, 192, etc., is reduced. In order toincrease the efficiency of the motor, the mass of gas which iscompressed back to theaccumulator pressure is designed .to be a minimum.When the, 31, 32, etc., rotates past the station 117, the compressedgases are returned back to the intake port 112 to be combined with morecompressed gases for another expansion work cycle.

In order to increase the motor torque per revolution an arcuate cutoffvalve 120 (FIG. 5) may be turned counterclockwise to give the desiredcutoff volume 191, 192, etc. For full admission, an arcuate valve 121may be turned counterclockwise. The compressed gases flow axially from achamber 122 through the arc ports into the working spaces 191, 192, etc.

In order to contain lubricating oil inside the drum 14 or 114, leafspring scrapers 130 (FIG. 6) may be used to scrape the oil of the vanes31, 32, etc., and keep it inside the drum 14 for lubricating the pivotshafts 41, 42, 43, 44, 45, 46, 47, 48, thebearings for the hub-shaft 12and the bearings 18 and 19 for the drum-l4. The

scrapers 130 may be secured to each bridge section 71, i

72, 73, 74, 75, 76, 77, 78, by means of screws 131 and a nut plate 132or a quick disconnect clamp. The beam section 14 has an arcuate surfacefor the spring 130 to follow as it flexes; so it will have fatiguestresses which are below the endurance limit of the spring steel 130. Asthe vanes 31, 32, etc., reciprocate and oscillate in the slots 61, 62,etc., the leaf spring scrapes the excess lubricating oil of the vanes31, 32, etc., so it will be contained inside the drum 14; justsufficient oil is left on the vane 31, 32, etc., to lubricate therubbing surface between the vanes 31, 32, etc., and the slots 61, 62,etc.

In order to limit the flow of compressed gas into the drum 14 to aminimum, seal bars 200 may be provided in axial slots 201 in the ends ofthe beam arcs 71, etc., that bear on the vanes 31 to 38. Metal springs202 or other fluidpressure means may be used to keep the seal bars 200tight against the vanes, and the bars 200 fit snugly in the axial slots201, thus a minimum flow of compressed gas passes from the working space91-98 into the drum 14. v

The geometry of the rotary vanes is illustrated in FIG.

8. When a vane 31 is in its zero 0 position, the radial line R from thecenterline of the drum 14 passes through the centerline of the hub-shaft12 and through the pivot point of this vane 31. This radial line R alsopasses through the centerline of the vane 31 and is collinear with theradial line r from the centerline of the hub-shaft 12. Thus, the angle abetween the centerline of the vane 31 and the radial line r is also zerowhen 0 0. P, r+ I P, maximum.

As the hub-shaft 11 and the drum 14 rotate clockwise, the angle orincreases, and the blade tip leads the rotoryand the radial lines r andR remain parallel to each other. The vane 31 (whose length is I) bearson the drum 14 (R) at a distance e from the pivot point. Thus, thetip ofthe vane I will be at a radial distance P, from the centerline of thehub. As the vane rotates from its 6 0 position to its 0 90 1r/2 radiansposition, the angle a increases and reaches a maximum when 0= 90;likewise, the radial distance P, is a minimum when 0 90.

As the vane rotatespast its 9 90 position, the angle or decreases, andthe radial distance P, increases until 0 l80 7r radians, where P, r I P,maximum again, and where a 0 again.

As the vane rotates past its 6 position,'the angle or becomes negative,and the vane tip lagsbehind the rotor. The radial lines r and R remainparallel to each other, and the radial distance P, from the hubcenterline to the tip of the vane I again decreases until the vanereaches its 0 270 position, where P, is at its minimum radial positionagain and the angle a is at its negative maximum.

As the vane rotates past its 0 270 31r/2 position, the angle 0:decreases and the radial distance P, increases until 0 360 211' radians,where P, r l P, maximum again, and a 0 agaimThe cycle for one vane isthen completed and will be repeated.

All of the vanes 32, 33, 34, 35, 36, 37, 38, undergo the same cycleasthe vane 31. If there are n vanes, they may be placed 21r/n radiansapart, so that there will be equal working spaces between vanes.

The surface which the vane tips circumscribe as they rotate andoscillate about the hub shaft can be derived mathematically; they can bewritten in polar coordinates with the origin at the centerline of thehub-shaft 12. For a prescribed design, the only variable is the angle 0.The angle 0 is zero when a radial line drawn from the centerline of thedrum first passes through the centerline of the hub shaft then throughthe pivot point of the vane and through the centerline of the vane. Thevane is in its straight line extended position at 0 and P r 1 which isat its largest radius.

The fixed parameters for a prescribed design are: c the distance betweenthe centerlines of the drum and the hub shaft. h the width of the slotin which the vane recipro' cates and oscillates. I the length of thevane from its pivot point to its extended position. r= the radialdistance from the hub centerline to the vane pivot point, and R theradius of the drum where the drum bears on the vane. The variableparameters are:

the distance from the vane pivot point to its slot bearing point at R. lthe thickness of the vane at e. P the radius from the hub centerline tothe vane tip. V 0 the angle of the hub and drum measured from the radialline drawn from the drum centerline to the centerline of the hub shaft.The equation for the radius of the circumscribed surface of the vane tipwith its origin at the hub centerline The equation for the distance fromthe vane pivot point to the point where the drum bears on the drum is:

The equation for the thickness of the vane is:

csin6 These equations may be derived as follows: The distances betweenthe parallel radial lines R and r at angle 0:

s 0 sin 0.

The chord segment distance a for the vane contact at radius R to thevane pivot point at a (R-r) sin 6 The minimum distance I) from the vanepivot point to the chord. a line normal to the chord:

b (R-r) cos 0 c The hypotenuse e of the triangle abe:

e a h (R-r) (sin 0 cos 0) 2(Rr) 0 cos 0 +0 This gives the secondequation shown above. The sine of the angle a between the radial line rand 5 the vane centerline 1:

The cosine law is used to get the radius of curvature P, of the surfacecircumscribed by the vane with respect to the star shaft centerline.

cos a V 1-sin a which is the first equation given above.

The angle B between the vane and the radial line R:

' For a constant slot I1 in the drum at radius R, to determine the vanethickness I with respect to the distance H e from the vane pivot point,so that it will fit snugly in h:

= P /sin a sin (b r/P sin a The area A at 0,:

A, z A (le,) (rlP sin a, [l (r/P,,) sin a, tan 01,]

The area A,, of the working space for n vanes of constant thickness 1:

sin a; [1( :x sin or tan 02 11} The working space or working volume is Vthe working area times the width of the vane s.

An integral vane compressor and vane motor 30 is shown in FIG. 9. It hasa compressor intake port3ll, a compressor exhaust port 312, a motorintake po 313', and a motor exhaust port 314.

The compressor intake port 311 to each working space is. closed bya'vane after that working space achieves its largest volume,v lowpressure gas being compressed in that working space as it is madesmaller. The compressed gas, after it has been compressed to a desiredpressure level, is discharged through the compressor exhaust 312, thecompressor exhaust port 312 being passed by the vane just before theworking space achieves its smallest volume.

The vane then opens the working space to high pressure gas flowing intothe motor intake port 313 just after the working space passes itssmallest volume. The motor intake port 313 remains open until the spacebetween the vanes is at a prescribed value, then the next vane moving toclose the working space off from the intake port 3l3 traps compressedgas in the working space. The working space increases in volume,'and thecompressed gas expands to do work on the vanes and membersrotatingtherwith until the working space is near its largest volume; Ithen the working space is opened by a vane to the motor exhaust port314, so that the expanded gases are exhausted. The momentum of the hotgases forces them to flow out radially andtangentially, or flow out inradial and tangential directions, while a fan or other device scavengesthe hot gases, axially or otherwise, so that afresh charge is blown intothe working space where it enters the compressor intake port 311. v

To those skilled in the art to which this invention relates, manychanges in construction and widely differing embodiments andapplications of the invention will suggest themselves withoutdepartingfrom the spirit and scope of the invention. The disclosures andthe description herein are purely illustrative and are not intended tobe in any sense limiting.

I claim: v

1. An integral vane-compressor and vane motor having compressor intakeport means and :exhaust port means and motor intake port means andexhaust port means, comprising: I

a rotating central hub having a series of vane pivot points spacedtherearound at equal radii-from the center of the hub, r

at least three vanes, each pinned atits center of gravity to said hub ata said pivot point,

a generally cylindrical drum with its axis parallel'to and displacedradially from that of said hub, said drum having a separate slot foreach vane through which the vane extends, for guiding the radialpositionof each said vane,

synchronizing means mechanically linking said hub and said drum so thatthey rotate in the same direction and at the same rotating speed. sothat said vanes reciprocate and oscillate in said guide slots as the huband drum rotate,

a housing enclosing said vanes and cooperating with said vanes and saiddrum to provide a series of working spaces, one for each said vane tocompress or expand afluid, and

intake and exhaust port means for leading fluid into andfrom saidworking spaces,

said compressor intake port means to each working space being closed bya said vane after that working space achieves its largest volume, lowpressure gas being compressed in said workingispace as it is madesmaller, the compressed gas, after it has been compressed to a desiredpressure level, being discharged through said compressor exhaust portmeans,

said compressor exhaust port means being passed by said vane just before'said working space achieves its smallest volume,

said vane then opening said working space to high pressure gas flowinginto said motor intake port means just after said working space passesits smallest volume, said motor intake port means remaining open untilthe space between said vanes is at a prescribed value, then the nextsaid vane moving to close said working space off from said intake portmeans and to trap compressed gas in said working space,

said working space increasing in volume and said compressed gasexpanding to do work on the vanes and members rotating therewith untilsaid working space is near its largest volume,

then said working space being opened by a said vane to said motorexhaust port means, so that said expanded gases are exhausted;

the centrifugal force of the hot gases forcing them to flow out radiallyand a fan for scavenging said hot gases axially so that a fresh chargeis blown into the working space where it enters said compressor intakeport means.

2. An integral vane compressor and vane motor having compressor intakeport means and exhaust port means and motor intake port means andexhaust port means, comprising? a rotating central hub having a seriesof vane pivot points spaced therearound at equal radii from the centerof the hub,

at least three vanes, each pinned at its center of gravity to said hubat a said pivot point,

a generally cylindrical drum with its axis parallelto and displacedradially from that of said hub, said drum having a separate slot foreach vane through which the vane extends, for guiding the radialposition of each said vane,

synchronizing means mechanically linking said hub and said drum so thatthey rotate in the same direction and at the same rotating speed, sothat said vanes reciprocate and oscillate in said guide slots as the huband drum rotate,

a housing enclosing said vanes and cooperating with said vanes and saiddrum to provide a series of working spaces, one for each said vane tocompress or expand a fluid, and

intake and exhaust port means for leading fluid into and from saidworking spaces.

said compressor intake port means to each working space being closed bya said vane after that working space achieves its largest volume, lowpressure gas being compressed in said working space as it is madesmaller, the compressed gas, after it has been compressed to a desiredpressure level, being discharged through said compressor exhaust portmeans,

said compressor exhaust port means being passed by said vane just beforesaid working space achieves its smallest volume,

said vane then opening said working space to high pressure gas flowinginto said motor intake port means just after said working space passesits smallest volume, said motor intake port means remaining open untilthe space between said vanes is at a prescribed value, then the nextsaid vane moving to close said working space off from said intake portmeans and to trap compressed gas in said working space,

said working space increasing in volume and said compressed gasexpanding to do work on the vanes and members rotating therewith untilsaid working space is near its largest volume,

then said working space being opened by a said vane to said motorexhaust port means. so that said expanded gases are exhausted;

the momentum of the hot gases forcing them to flow out in a radial andtangential direction, and

means for scavenging said hot gases so that a fresh charge is blown intothe working space where it enters said compressor intake port means.

1. An integral vane compressor and vane motor having compressor intakeport means and exhaust port means and motor intake port means andexhaust port means, comprising: a rotating central hub having a seriesof vane pivot points spaced therearound at equal radii from the centerof the hub, at least three vanes, each pinned at its center of gravityto said hub at a said pivot point, a generally cylindrical drum with itsaxis parallel to and displaced radially from that of said hub, said drumhaving a separate slot for each vane through which the vane extends, forguiding the radial position of each said vane, synchronizing meansmechanically linking said hub and said drum so that they rotate in thesame direction and at the same rotating speed, so that said vanesreciprocate and oscillate in said guide slots as the hub and drumrotate, a housing enclosing said vanes and cooperating with said vanesand said drum to provide a series of working spaces, one for each saidvane to compress or expand a fluid, and intake and exhaust port meansfor leading fluid into and from said working spaces, said compressorintake port means to each working space being closed by a said vaneafter that working space achieves its largest volume, low pressure gasbeing compressed in said working space as it is made smaller, thecompressed gas, after it has been compressed to a desired pressurelevel, being discharged through said compressor exhaust port means, saidcompressor exhaust port means being passed by said vane just before saidworking space achieves its smallest volume, said vane then opening saidworking space to high pressure gas flowing into said motor intake portmeans just after said working space passes its smallest volume, saidmotor intake port means remaining open until the space between saidvanes is at a prescribed value, then the next said vane moving to closesaid working space off from said intake port means and to trapcompressed gas in said working space, said working space increasing involume and said compressed gas expanding to do work on the vanes andmembers rotating therewith until said working space is near its largestvolume, then said working space being opened by a said vane to saidmotor exhaust port means, so that said expanded gases are exhausted; thecentrifugal force of the hot gases forcing them to flow out radially anda fan for scavenging said hot gases axially so that a fresh charge isblown into the working space where it enters said compressor intake portmeans.
 2. An integral vane compressor and vane motor having compressorintake port means and exhaust port means and motor intake port means andexhaust port means, comprising: a rotating central hub having a seriesof vane pivot points spaced therearound at equal radii from the centerof the hub, at least three vanes, each pinned at its center of gravityto said hub at a said pivot point, a generally cylindrical drum with itsaxis parallel to and displaced radially from that of said hub, said drumhaving a separate slot for each vane through which the vane extends, forguiding the radial position of each said vane, synchronizing meansmechanically linking said hub and said drum so that they rotate in thesame direction and at the same rotating speed, so that said vanesreciprocate and oscillate in said guide slots as the hub and drumrotate, a housing Enclosing said vanes and cooperating with said vanesand said drum to provide a series of working spaces, one for each saidvane to compress or expand a fluid, and intake and exhaust port meansfor leading fluid into and from said working spaces, said compressorintake port means to each working space being closed by a said vaneafter that working space achieves its largest volume, low pressure gasbeing compressed in said working space as it is made smaller, thecompressed gas, after it has been compressed to a desired pressurelevel, being discharged through said compressor exhaust port means, saidcompressor exhaust port means being passed by said vane just before saidworking space achieves its smallest volume, said vane then opening saidworking space to high pressure gas flowing into said motor intake portmeans just after said working space passes its smallest volume, saidmotor intake port means remaining open until the space between saidvanes is at a prescribed value, then the next said vane moving to closesaid working space off from said intake port means and to trapcompressed gas in said working space, said working space increasing involume and said compressed gas expanding to do work on the vanes andmembers rotating therewith until said working space is near its largestvolume, then said working space being opened by a said vane to saidmotor exhaust port means, so that said expanded gases are exhausted; themomentum of the hot gases forcing them to flow out in a radial andtangential direction, and means for scavenging said hot gases so that afresh charge is blown into the working space where it enters saidcompressor intake port means.